JP4818756B2 - Timer valve - Google Patents

Description

  The present invention relates to a timer valve suitable for measuring a switching time between initial water discharge and specified pressure water discharge in a stage water discharge automatic valve device that is installed in a tunnel such as a highway, for example, and realizes step water discharge.

  In the conventional stage water discharge automatic valve device, the pressure control valve is used to switch from the initial water discharge to the specified pressure water discharge after elapse of a predetermined delay time (see, for example, Patent Document 1). In this pressure regulating valve, a disc is slidably provided in the cylinder, and the inside of the cylinder is divided into an upper cylinder chamber and a lower cylinder chamber. The upper cylinder chamber and the lower cylinder chamber communicate with each other through a pipe, and a needle valve is provided in the middle of the pipe. Further, a check valve is provided on the disc, and when the secondary pressurized water is introduced into the cylinder, it flows from the upper cylinder chamber to the lower cylinder chamber to be filled. The check valve prevents the flow of water from the lower cylinder chamber to the upper cylinder chamber against the lowering of the disc when the secondary pressure is applied to the upper cylinder chamber in a state where water is filled. The moving speed of the disc is determined by the flow rate of a needle valve that allows water to flow from the lower cylinder chamber to the upper cylinder chamber via a pipe. Therefore, the flow rate of the needle valve is set to a predetermined flow rate, and the secondary side pressurized water is introduced into the cylinder in a state where water is filled to control the switching time (delay time) from the initial water discharge to the specified pressure water discharge. .

JP 2005-248970 A

Since the conventional pressure regulating valve supplies secondary side pressurized water to the cylinder to lower the disc, there is a problem that the delay time varies due to the pressure variation of the secondary side pressurized water.
In addition, the flow rate of the needle valve provided in the middle of the piping that connects the upper cylinder chamber and the lower cylinder chamber is adjusted to control the speed of the disk that descends in the cylinder, so the wall surface of the piping and the fluid There is also a problem that the influence of the viscosity of the fluid is increased due to the friction between the fluid and the fluid, that is, the influence of the temperature characteristic of the fluid is increased, and the set time varies.

  The present invention has been made in order to solve the above-described problems. The spring force of the operating spring is used as a driving force to eliminate the influence of pressure fluctuation of the pressurized water, and further, the brake partition plate is formed by a plate orifice. The purpose is to obtain a timer valve that can easily and accurately measure time by controlling the descending speed of the fluid to eliminate the influence of the temperature characteristics of the fluid.

The timer valve according to the present invention is slidably disposed in the axial direction in the cylinder and defines the inside of the cylinder into a pressurizing chamber on one side in the axial direction and a piston chamber on the other side, A first piston that moves from a first position where the volume of the pressurizing chamber is reduced by supplying a pressurizing medium to the pressurizing chamber to a second position where the volume of the pressurizing chamber is expanded, and the first piston A second piston disposed in the piston chamber so as to be capable of reciprocating in the axial direction of the cylinder between the first piston and a third position spaced a predetermined distance from the first piston toward the non-pressurizing chamber. An operating spring that is contracted between the piston and the second piston to urge the second piston to be positioned at the third position, and the supply of the pressurized medium to the pressurizing chamber is stopped. when it is, the first piston via the actuating spring and the second piston From serial second position and a, a return spring for urging the second piston so as to return to the first position. Further, the cylinder is provided adjacent to the anti-pressurization chamber side of the piston chamber, and a fluid chamber filled with fluid is disposed in the fluid chamber so as to be slidable in the axial direction of the cylinder. The fluid chamber is defined as a first fluid chamber on the piston chamber side and a second fluid chamber on the anti-piston chamber side, and a plate orifice is provided for communicating the first fluid chamber and the second fluid chamber. A partition plate, a shaft to which the brake partition plate is fixed and inserted through the fluid chamber so as to be movable in the axial direction of the cylinder, one end of which is fixed to the second piston, and the fluid chamber And a valve body that is pressed by the shaft to take a valve open or closed state, and an on-off valve that has a spring that returns the valve body to a closed or open state. .

  According to the present invention, when the pressurizing medium is supplied to the pressurizing chamber, the first piston moves from the first position to the second position. At this time, the brake partition plate moves when the fluid flows from the second fluid chamber into the first fluid chamber through the plate orifice, so that the moving speed of the braking partition plate, that is, the moving speed of the second piston is increased. Is extremely slow. As a result, instead of moving the second piston, the operating spring contracts. As a result, the driving force is stored in the operating spring. When the first piston is located at the second position, the activation force is released to the operating spring, and the second piston is moved while receiving the resistance force of the return spring and the resistance force of the fluid acting on the braking partition plate. Move to the third position. Therefore, the amount of extension of the shaft from the fluid chamber is maximized, the valve body is pressed against the stored force of the spring, and the on-off valve is opened or closed.

Thus, the pressurizing medium contributes to move the first piston from the first position to the second position, and the time until the on-off valve is opened or closed from the open state or the closed state is the operating spring. It is determined by the starting force stored in and the resistance force of the fluid acting on the braking partition plate. Therefore, even if the pressure of the pressurized medium fluctuates rapidly, the above time is not affected at all.
Further, since the brake partition plate moves when the fluid flows from the second fluid chamber into the second fluid chamber via the plate orifice, the moving speed of the brake partition plate is not easily affected by the temperature characteristics of the fluid. The time is stable regardless of the environmental temperature.

  FIG. 1 is a sectional view showing the configuration of a timer valve in one embodiment of the present invention, FIG. 2 is a sectional view for explaining the operation of the timer valve in one embodiment of the present invention, and FIG. The state at the time of starting of a timer valve is shown, and (b) of Drawing 2 shows the state at the time of operation of a timer valve. FIG. 3 is a block diagram showing a stage water discharge automatic valve device to which the timer valve of the present invention is applied.

  In FIG. 1, a pair of first and second cylinders 1 and 2 each formed in a bottomed cylindrical shape are clamped and fixed with a separator 3 sandwiched with an opening facing each other. The first piston 4 formed in a bottomed cylindrical shape is slidable in the first cylinder 1 with the opening directed toward the separator 3 and reciprocally movable in the axial direction of the first cylinder 1. The first cylinder 1 is defined by a pressurizing chamber 8 and a piston chamber. Further, the second piston 5 formed in a bottomed cylindrical shape is disposed in the piston chamber, that is, in the first piston 4 with the opening facing the separator 3. The operating spring 6 is contracted between the inner bottom surface of the first piston 4 and a flange portion 5 a that protrudes radially outward from the opening edge of the second piston 5. Further, the return spring 7 is contracted between the inner bottom surface of the second piston 5 and the separator 3.

Here, the pressurizing chamber 8 is constituted by the first cylinder 1 and the first piston 4, and pressurized water as a pressurizing medium is supplied to the pressurizing chamber 8 through a port P <b> 3 formed at the bottom of the first cylinder 1. It can be done. Further, an air hole 9 is formed in the first cylinder 1 so as to communicate the space (piston chamber) on the side of the anti-pressurization chamber in the first cylinder 1 defined by the first piston 4 and the outside. Yes. Further, a first piston position adjusting bolt 10 is screwed to the bottom of the first cylinder 1 with its axial direction coinciding with the axial direction of the first cylinder 1.
Further, the spring force of the operating spring 6 is set larger than the spring force of the return spring 7. In the initial state where pressurized water is not supplied to the pressurizing chamber 8, the flange portion 5 a of the second piston 5 is in contact with the flange portion 4 a of the first piston 4 by the biasing force of the operating spring 6. That is, the second piston 5 is located at the third position. Further, in the initial state, the first piston 4 is in contact with the end portion of the first piston position adjusting bolt 10 that extends into the pressurizing chamber 8 by the urging force of the return spring 7. That is, the first piston 4 is located at the first position.

  The fluid chamber 11 is a sealed space constituted by the second cylinder 2 and the separator 3, and is filled with silicone oil 12 as a fluid. The shaft 13 penetrates the fluid chamber 11 and is disposed so as to be able to reciprocate in the axial direction of the second cylinder 2. One end of the shaft 13 is fixed to the bottom of the second piston 5, and the other end extends to the on-off valve 17 described later. Further, an O-ring is interposed between the shaft 13 and the separator 3 and further between the shaft 13 and the bottom of the second cylinder 2 so that the silicone oil 12 can be prevented from leaking and slidably moved. It has become.

  The brake partition plate 14 is arranged on the shaft 13 so as to separate the fluid chamber 11 in the axial direction of the second cylinder 2 into a first fluid chamber 11a on the first cylinder side and a second fluid chamber 11b on the side opposite to the first cylinder. It is fixed. The braking partition plate 14 slides and moves on the inner peripheral wall surface of the second cylinder 2 in conjunction with the movement of the shaft 13. Further, a plate orifice 15 is formed in the braking partition plate 14 so as to communicate the first and second fluid chambers 11a and 11b. Further, a check valve 16 is formed on the braking partition plate 14. The check valve 16 prevents the silicone oil 12 from flowing into the first fluid chamber 11a from the second fluid chamber 11b when the shaft 13 moves (lowers) toward the on-off valve 17 side, and the shaft 13 is pressurized. The inflow of the silicone oil 12 from the first fluid chamber 11a to the second fluid chamber 11b when moving (raising) to the 8 side is allowed.

  The on-off valve 17 is a valve body that opens and closes the input port P1, the output port P2, the valve body 18 that opens and closes between the input port P1 and the output port P2, and the input port P1 and the output port P2. And a spring 19 that urges 18 and is normally open. The on-off valve 17 is closed between the input port P1 and the output port P2 by the spring force of the operating spring 6 that acts on the valve body 18 via the shaft 13.

Next, the operation of the timer valve 100 configured as described above will be described.
First, in the initial state, as shown in FIG. 1, the flange portion 5 a of the second piston 5 is in contact with the flange portion 4 a of the first piston 4 by the biasing force of the operating spring 6. Further, the first piston 4 is in contact with the extending end of the first piston position adjusting bolt 10 into the pressurizing chamber 8 by the urging force of the return spring 7. That is, the first piston 4 is located at the upper limit set by the first piston position adjusting bolt 10.

  Next, when pressurized water is supplied into the pressurizing chamber 8 from the port P3 and the pressurizing chamber 8 is filled, a force for lowering the first piston 4 is generated. This downward force is transmitted to the shaft 13 via the first piston 4, the operating spring 6 and the second piston 5, and acts to lower the shaft 13. Then, as the shaft 13 is lowered, the braking partition plate 14 is lowered. At this time, the silicone oil 12 in the second fluid chamber 11b is blocked from flowing into the first fluid chamber 11a from the check valve 16 and flows into the first fluid chamber 11a from the plate orifice 15. As a result, a large resistance acts on the braking partition plate 14. Therefore, as shown in FIG. 2A, instead of the second piston 5 descending, the operating spring 6 contracts, and the first piston 4 has a lower limit (the flange portion 4a abuts against the separator 3). Descends to the second position). As a result, the driving force of the timer valve is stored in the operating spring 6.

  Next, the contracted operating spring 6 extends while receiving the resistance force of the silicone oil 12 and the reaction force of the return spring 7, that is, the stored force of the operating spring 6 is released. The second piston 5, the shaft 13, and the braking partition plate 14 are lowered in conjunction with the extension operation of the operating spring 6. At this time, the silicone oil 12 in the second fluid chamber 11b flows into the first fluid chamber 11a from the plate orifice 15 as the braking partition plate 14 is lowered, so that the shaft 13, that is, the second piston 5 gradually descends. To do. Then, as shown in FIG. 2B, when the flange portion 5 a of the second piston 5 is lowered until the flange portion 4 a comes into contact with the flange portion 4 a of the first piston 4, the shaft 13 pushes the valve element 18 against the biasing force of the spring 19. The flow path between the input port P1 and the output port P2 is closed. At this time, the return spring 7 is contracted, and the return force is stored.

  Next, when the supply of pressurized water from the port P3 is stopped, the downward force acting on the first piston 4 disappears. Therefore, the stored power of the return spring 7 is released. In other words, the contracted return spring 7 extends to raise the second piston 5 and raise the shaft 13. At this time, the silicone oil 12 in the first fluid chamber 11a mainly flows from the check valve 16 into the second fluid chamber 11b. As a result, a large resistance force does not act on the braking partition plate 14 and the braking partition plate 14 rises quickly. Therefore, the first piston 4 rises together with the second piston 5, contacts the extension end of the first piston position adjusting bolt 10 into the pressurizing chamber 8, and returns to the initial state.

In the timer valve 100 configured in this manner, the initial position of the first piston 4 can be changed by changing the amount of advancement / retraction of the first piston position adjusting bolt 10, that is, by changing the extension amount into the pressurizing chamber 8. (First position) is changed. Thereby, since the length of the return spring 7 is changed, the stroke amount of the shaft 13 is changed, and the valve closing time from the supply of pressurized water to the closing of the on-off valve 17 is changed.
Further, when the braking partition plate 14 is lowered, the silicone oil 12 in the second fluid chamber 11 b flows into the first fluid chamber 11 a through the plate orifice 15 provided in the braking partition plate 14. Accordingly, the lowering speed of the brake partition plate 14 is not affected by the viscosity of the fluid, that is, the temperature characteristic of the fluid, and is controlled by the diameter of the plate orifice 15.
Therefore, since the diameter of the plate orifice 15 is determined, the valve closing time of the on-off valve 17 can be simply adjusted simply by adjusting the extension amount of the first piston position adjusting bolt 10 into the pressurizing chamber 8. Can be set. In addition, the set valve closing time is stable regardless of the environmental temperature.

  The pressurized water lowers the first piston 4 to the lower limit and does not act to lower the shaft 13. That is, the shaft 13 is lowered by the driving force stored in the operating spring 6 when the first piston 4 is lowered to the lower limit by the supply of pressurized water. Therefore, the pressure fluctuation of the pressurized water does not affect the closing time of the on-off valve 17 at all.

  In the above description, the normally open type on-off valve 17 is used to measure the valve closing time. However, the normally open type on-off valve may be used to measure the valve opening time.

Next, the effect of the timer valve 100 will be described using the stage water discharge automatic valve device shown in FIG.
In FIG. 3, the stage water discharge automatic valve device includes an automatic valve 200 that adjusts the flow rate of primary-side pressurized water flowing from the primary-side flow path 22 to the secondary-side flow path 23 by changing the opening of the main valve 26, and the primary valve Timer valve 100 for switching the opening degree of the main valve 26 from the initial opening degree to the set opening degree after the elapse of a predetermined delay time, the main valve driving mechanism of the main valve 26 of the automatic valve 200, and the timer valve 100. The control valve 300 controls the opening degree of the main valve 26 to a set opening degree by sensing that the pressure of the secondary side pressurized water has reached a predetermined pressure. Pressure pilot valve 400.

First, the structure of the automatic valve 200 will be described.
The valve body 21 includes a primary side flow path 22 to which a primary side pipe (not shown) is connected, a secondary side flow path 23 to which a secondary side pipe (not shown) is connected, and a primary side flow path 22. A communication hole 24 that communicates with the secondary side flow path 23, a shaft centered with the hole center of the communication hole 24, and the secondary side flow path 23 across the communication hole 24. And a cylindrical cylinder 25 formed so as to open to the secondary flow path 23.

  The main valve 26 includes a disk portion 27, four guide portions 28 extending in the axial direction of the main valve 26 at an equiangular pitch in the circumferential direction from the vicinity of an edge on one side of the disk portion 27, and the disk portion 27 is provided with a stem fitting recess 29 that is recessed at one side center portion, and an O-ring 30 that is fitted to the outer peripheral portion of the disk portion 27. The main valve 26 is slidably mounted by inserting the guide portion 28 into the communication hole 24 from the primary channel 22 side.

  The guide rod 31 protrudes from the other central portion of the disk portion 27 and is slidably fitted into a rod insertion hole 32 a formed in the lid body 32. An O-ring 33 is interposed between the guide rod 31 and the rod insertion hole 32a to prevent fluid from leaking from the primary channel 22 through the rod insertion hole 32a. Further, the spring 34 is contracted between the disk portion 27 and the lid body 32 to press the disk portion 27 toward the secondary side flow path 23. As a result, the O-ring 30 is in close contact with the valve seat 24 a formed by the outer peripheral edge of the communication hole 24, and the flow path between the primary side flow path 22 and the secondary side flow path 23 is closed. Further, by the operation of a piston 36 described later, the guide rod 31 is guided to the rod insertion hole 32a and moves to the left in FIG. 3, the main valve 26 is separated from the valve seat 24a, and the primary side flow path 22 and the secondary channel 22 The flow path between the side flow paths 23 is opened. Each O-ring is provided to prevent fluid leakage, and the description thereof is omitted below.

  The cylinder lid 35 is attached to the valve body 21 with an O-ring interposed so as to close the opening of the cylinder 25 on the side opposite to the secondary flow path 23. The piston 36 is slidably inserted into the cylinder 25, the O-ring 37 is fitted to the outer periphery of the piston 36, and the inside of the cylinder 25 is connected to the piston chamber 25a on the secondary channel 23 side and the cylinder lid. It is partitioned into a working chamber 25b on the 35 side. Further, a stopper 38 is provided in a radially protruding manner over the entire circumference in the opening end of the inner wall surface of the cylinder 25 on the secondary flow path 23 side, and the piston 36 moves to the secondary flow path 23 side. The amount is regulated. An inflow / outflow passage 39 is formed in the cylinder lid 35 so as to communicate the working chamber 25b with the outside. Furthermore, the stem 40 is attached so that one end is fixed to the center position of the piston 36 and the other end is fitted into the stem fitting recess 29 of the disk portion 27 so that the axis thereof coincides with the axis of the cylinder 25. It has been. Here, the main valve drive mechanism is constituted by the cylinder 25, the spring 34, the cylinder lid 35, the piston 36, the stem 40, and the like.

The cylinder lid 35 has an opening that is coaxial with the axis of the cylinder 25. A cylindrical case 41 is attached coaxially with the axis of the cylinder 25 with a flange portion formed on one end side of the case 41 interposed in an opening of the cylinder lid 35 with an O-ring interposed. . Further, a drain port 42 is formed so as to communicate between the inside and outside of the case 41.
The lift setting adjuster 43 is manufactured in a cylindrical shape, and is screwed into a female screw portion formed on the inner wall surface on the other end side of the case 41 so as to be freely moved forward and backward. A through hole 44 is formed so as to communicate with the inside and outside of the adjuster 43. A pair of O-rings 45 are interposed between the inner peripheral wall surface of the case 41 and the outer peripheral wall surface of the adjuster 43 so as to be spaced apart from each other by a predetermined distance in the axial direction and sandwich the drain port 42 and the through hole 44.

A small diameter portion is formed in the center hole 47 at a position on the other end side of the through hole 44 of the adjuster 43. One end of the shaft 46 is fixed to the piston 36, and the other end is inserted into the small diameter portion of the center hole 47 of the adjuster 43 so as to coincide with the axis of the cylinder 25. The small diameter portion serves as a guide, and the shaft 46 moves in the axial direction of the cylinder 25 in conjunction with the movement of the piston 36. At this time, the large diameter portion 46 a projecting from one end of the shaft 46 slides on the inner wall surface of the center hole 47 of the adjuster 43.
Here, the case 41, the adjuster 43, the shaft 46, and the like constitute a stop control mechanism. The case 41 and the adjuster 43 correspond to a guide member, and the center hole 47 of the adjuster 43 corresponds to a guide hole.

  In addition, by changing the advance / retreat amount of the adjuster 43 with respect to the case 41, the large diameter portion 46a is removed from the center hole 47 of the adjuster 43 from the initial state (the sliding relationship between the large diameter portion 46a and the center hole 47 is lost). The stroke amount of the piston 36 is changed. That is, the initial opening degree of the main valve 26 is adjusted by adjusting the advance / retreat amount of the adjuster 43 with respect to the case 41.

The pressure regulation pilot valve 400 is a normally closed type, and operates and opens when the pressure of the secondary side pressurized water in the secondary side flow path 23 reaches a predetermined pressure. That is, by adjusting the operating pressure of the pressure regulation pilot valve 400, the pressure of the specified pressure water discharge is adjusted.
Here, one end of the first pipe 50 is connected to the primary flow path 22 of the automatic valve 200 via the start valve 300, and the other end is connected to the port P <b> 3 of the timer valve 100. The branch pipe 51 branches from the downstream side of the start valve 300 of the first pipe 50 and is connected to the inflow / outflow passage 39 of the automatic valve 200 and the input port of the pressure regulating pilot valve 400. Further, the second pipe 52 has one end connected to the secondary flow path 23 of the automatic valve 200 and the other end connected to the working chamber of the pressure regulating pilot valve 400. Further, the third pipe 53 has one end connected to the drain port 42 of the automatic valve 200 and the other end connected to the input port P1 of the on-off valve 17. The plate orifice 54 is disposed on the start valve 300 side of the connection portion of the first pipe 50 with the branch pipe 51.

Next, the operation of the stage water discharge automatic valve device configured as described above will be described.
First, when the start valve 300 is activated, the primary pressurized water in the primary channel 22 flows into the working chamber 25b via the first pipe 50, the branch pipe 51, and the inflow / outflow channel 39, and is filled. At this time, inflow of the primary side pressurized water into the center hole 47 of the adjuster 43 is blocked by the large diameter portion 46a, the pressure in the working chamber 25b rises, and the piston 36 moves to the left in FIG. The moving force of the piston 36 is transmitted to the main valve 26 via the stem 40, and the main valve 26 moves to the left in FIG. 3 against the urging force of the spring 34. When the large diameter portion 46 a comes out of the center hole 47 of the adjuster 43, the working chamber 25 b is communicated with the third pipe 53 via the through hole 44 and the drain port 42. Therefore, the primary pressurized water that has flowed into the working chamber 25 b from the inflow / outflow channel 39 flows into the third pipe 53 through the through hole 44 and the drainage port 42. And the primary side pressurized water which distribute | circulated the inside of the 3rd piping 53 flows in into the normally open type on-off valve 17 from the input port P1, and is drained from the output port P2. Therefore, the pressure in the working chamber 25b is kept constant, no further moving force acts on the piston 36, and the main valve 26 is maintained at the initial opening.

  Therefore, the primary side pressurized water flows into the secondary side flow path 23 from the primary side flow path 22. Then, the primary side pressurized water is filled in the secondary side flow path 23, becomes secondary side pressurized water, flows through the secondary side pipe (not shown), and is discharged from a water spray nozzle (not shown). At this time, water discharged from the water spray nozzle becomes low-pressure water discharge.

  On the other hand, simultaneously with the operation of the start valve 300, the primary side pressurized water in the primary side flow path 22 flows through the first pipe 50 and is supplied from the port P 3 of the timer valve 100 to the pressurizing chamber 8. When the primary side pressurized water fills the pressurizing chamber 8, the first piston 4 starts to descend. The lowering force of the first piston 4 is transmitted to the second piston 5 via the operating spring 6 and acts to lower the shaft 13. At this time, the check valve 16 is closed and a large resistance force of the silicone oil 12 is generated. Therefore, instead of the second piston 5 descending, the operating spring 6 contracts and the first piston 4 descends to the lower limit.

  Next, the operating spring 6 extends while receiving the resistance force of the silicone oil 12 and the reaction force of the return spring 7. In conjunction with the extension operation of the operating spring 6, the silicone oil 12 in the second fluid chamber 11b flows from the plate orifice 15 into the first fluid chamber 11a, and the shaft 13, that is, the second piston 5, gradually descends. When the flange portion 5a of the second piston 5 is lowered until it abuts against the flange portion 4a of the first piston 4, the shaft 13 lowers the valve body 18 against the urging force of the spring 19, and the input port P1 and the output port The flow path between P2 is closed. At this time, the return spring 7 is contracted, and the return force is stored.

  Thereby, drainage of the primary side pressurized water from the output port P2 is stopped. Therefore, the pressure in the working chamber 25b rises again by the primary-side pressurized water flowing in from the inflow / outflow passage 39, and the piston 36 moves to the left in FIG. As a result, the main valve 26 is further opened, and the flow rate of the primary pressurized water flowing from the primary side flow path 22 into the secondary side flow path 23 increases.

The secondary pressurized water in the secondary flow path 23 is supplied to the working chamber of the pressure regulating pilot valve 400 via the second pipe 52. And if the pressure of the secondary side pressurized water in the secondary side flow path 23 becomes higher than a predetermined pressure, the pressure regulation pilot valve 400 will be opened. Thereby, the primary side pressurized water supplied into the working chamber 25 b of the automatic valve 200 via the branch pipe 51 is drained from the output port of the pressure regulating pilot valve 400. Therefore, the pressure in the working chamber 25b is kept constant, no further moving force acts on the piston 36, and the main valve 26 is maintained at the set opening.
Therefore, the primary side pressurized water flows from the primary side channel 2 into the secondary side channel 3, and the secondary side pressurized water having a predetermined pressure flows through the secondary side pipe and is discharged from the water spray nozzle. . At this time, the water discharged from the water spray nozzle becomes the specified pressure water discharge.

Next, when the start valve 300 is closed, there is no supply of the primary side pressurized water to the working chamber 25b of the automatic valve 200 via the branch pipe 51, and the primary side pressurized water in the working chamber 25b is supplied to the pressure regulating pilot valve 400. Drained from the output port. Therefore, the main valve 26 is closed by the biasing force of the spring 34, and the piston 36 moves to the initial state. At the same time, there is no supply of primary-side pressurized water from the port P3, the return force of the return spring 7 is released, and the second piston 5 and the shaft 13 start to rise. The first piston 4 rises in synchronization with the rise of the second piston 5. At this time, the check valve 16 is opened, and the silicone oil 12 quickly flows into the second fluid chamber 11b from the first fluid chamber 11a and returns to the initial state.
Then, the valve body 18 of the on-off valve 17 is raised by the urging force of the spring 19, the flow path between the input port P 1 and the output port P 2 is opened, and the primary side pressurized water is drained into the third pipe 53. Return to state.

  In this stage water discharge automatic valve device, by operating the start valve 300, the primary side pressurized water is supplied to the timer valve 100 to start the measurement of the delay time, and after the delay time has elapsed, the main valve 26 is changed from the initial opening to the set opening. Since it opens, it can transfer to regular pressure water discharge reliably after delay time progresses from initial water discharge.

  Further, the initial opening degree of the main valve 26 can be adjusted by changing the advance / retreat amount of the adjuster 43 with respect to the case 41. Further, the pressure of the specified pressure water discharge can be adjusted by changing the operating pressure of the pressure regulation pilot valve 400. Furthermore, the delay time can be adjusted by changing the advance / retreat amount of the first piston position adjusting bolt 10. Accordingly, the respective adjustments do not interfere with each other, and the on-site adjustment work is remarkably simplified.

In addition, since the timer valve 100 uses the primary side pressurized water only as a trigger for starting the measurement of the delay time and measures the delay time by the operating spring 6, even if the primary side pressurized water fluctuates rapidly, the delay time The delay time can be accurately measured without affecting the measurement.
In addition, the fluid chamber 11 is filled with the silicone oil 12, and the first fluid is supplied from the second fluid chamber 11b through the plate orifice 15 in which the silicone oil 12 is formed in the braking partition plate 14 while the braking partition plate 14 is moved. Since it is moved to the chamber 11a, the influence of the temperature characteristic of the fluid is eliminated, and the delay time can be measured accurately.
Although the silicone oil 12 is used as the fluid, the fluid is not limited to the silicone oil 12, and for example, water may be used.

It is sectional drawing which shows the structure of the timer valve in one Example of this invention. It is sectional drawing for demonstrating operation | movement of the timer valve in one Example of this invention. It is a block diagram which shows the stage water discharge automatic valve apparatus to which the timer valve of this invention is applied.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 1st cylinder, 4 1st piston, 5 2nd piston, 6 Acting spring, 7 Return spring, 8 Pressurizing chamber, 10 1st piston position adjustment bolt, 11 Fluid chamber, 11a 1st fluid chamber, 11b 2nd Fluid chamber, 13 shaft, 14 brake partition plate, 15 plate orifice, 16 check valve, 17 on-off valve, 18 valve body, 19 spring.

Claims (3)

A cylinder is slidably disposed in the axial direction of the cylinder, and the inside of the cylinder is divided into a pressurizing chamber on one side in the axial direction and a piston chamber on the other side, and pressurization to the pressurizing chamber is performed. A first piston that moves from a first position at which the volume of the pressurizing chamber is reduced by supplying a medium to a second position at which the volume of the pressurizing chamber is expanded;
A second piston disposed in the piston chamber so as to be capable of reciprocating in the axial direction of the cylinder between the first piston and a third position spaced a predetermined distance from the first piston toward the non-pressurizing chamber; ,
An operating spring that is contracted between the first piston and the second piston and biases the second piston to be positioned at the third position;
When the supply of the pressurizing medium to the pressurizing chamber is stopped, the first piston is returned from the second position to the first position via the operating spring and the second piston . A return spring that biases the two pistons;
A fluid chamber provided adjacent to the anti-pressurization chamber side of the piston chamber of the cylinder and filled with fluid;
The fluid chamber is slidably disposed in the axial direction of the cylinder in the fluid chamber, and defines the fluid chamber into a first fluid chamber on the piston chamber side and a second fluid chamber on the anti-piston chamber side. A braking partition plate provided with a plate orifice for communicating the fluid chamber and the second fluid chamber;
A shaft having the braking partition plate fixed and inserted through the fluid chamber so as to be movable in the axial direction of the cylinder, one end of which is fixed to the second piston;
An on-off valve that is disposed on the opposite cylinder side of the fluid chamber, has a valve body that is pressed by the shaft and takes a valve open or closed state, and a spring that returns the valve body to a closed or open state;
A timer valve characterized by comprising:   A check valve that allows the fluid to flow from the first fluid chamber to the second fluid chamber and prevents the fluid from flowing from the second fluid chamber to the first fluid chamber is used for the braking. The timer valve according to claim 1, wherein the timer valve is provided on the partition plate.   A position adjusting bolt is attached to the cylinder in a screwed state with its axial direction coinciding with the axial direction of the cylinder so that the extension amount into the pressurizing chamber is variable, and the first piston is moved to the return spring. 3. The timer valve according to claim 1, wherein the timer valve is positioned at the first position by being brought into contact with an extended end of the position adjusting bolt by an urging force.

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